Planetary gear train of automatic transmission for vehicles

ABSTRACT

A planetary gear train of an automatic transmission for a vehicle may include an input shaft receiving a torque of an engine, an output shaft disposed substantially in parallel with the input shaft at a predetermined distance and outputting a changed torque, a first planetary gear set disposed on the input shaft and including a first, second and third rotation elements, a second planetary gear set disposed on the output shaft and including a fourth, fifth and sixth rotation elements, four transfer gears forming the externally-meshed gears, and frictional elements including clutches connecting the input shaft and the rotation elements of the first and second planetary gear sets and brakes connecting the rotation elements of the first and second planetary gear sets and a transmission housing.

CROSS-REFERENCE TO RELATED APPLICATION

The present application claims priority of Korean Patent Application Number 10-2012-0124120 filed Nov. 5, 2012, the entire contents of which application are incorporated herein for all purposes by this reference.

BACKGROUND OF INVENTION

1. Field of Invention

The present invention relates to an automatic transmission for a vehicle. More particularly, the present invention relates to a planetary gear train of an automatic transmission for a vehicle that can improve mountability and power delivery performance and reduce fuel consumption.

2. Description of Related Art

Recently, vehicle makers direct all their strength to improve fuel economy due to worldwide high oil prices and strengthen of exhaust gas regulations.

Improvement of fuel economy may be achieved by multi-shift mechanism realizing greater number of shift speeds in an automatic transmission. Typically, a planetary gear train is realized by combining a plurality of planetary gear sets and friction elements.

It is well known that when a planetary gear train realizes a greater number of shift speeds, speed ratios of the planetary gear train can be more optimally designed, and therefore a vehicle can have economical fuel mileage and better performance. For that reason, the planetary gear train that is able to realize more shift speeds is under continuous investigation.

Though achieving the same number of speeds, the planetary gear train has a different operating mechanism according to a connection between rotation elements (i.e., sun gear, planet carrier, and ring gear). In addition, the planetary gear train has different features such a durability, power delivery efficiency, and size depend on the layout thereof. Therefore, designs for a combining structure of a gear train are also under continuous investigation.

If the number of shift-speeds, however, increases, the number of components in the automatic transmission also increases. Therefore, mountability, cost, weight and power delivery efficiency may be deteriorated.

Particularly, since the planetary gear train having a number of components is hard to be mounted in a front wheel drive vehicle, researches for minimizing the number of components have been developed.

The information disclosed in this Background section is only for enhancement of understanding of the general background of the invention and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person skilled in the art.

SUMMARY OF INVENTION

The present invention has been made in an effort to provide a planetary gear train of an automatic transmission for a vehicle having advantages of improving mountability by shortening a length thereof and reducing the number of components as a consequence of achieving nine forward speeds and one reverse speed by disposing two planetary gear sets separately on an input shaft and an output shaft disposed in parallel or substantially in parallel and connecting rotation elements of the planetary gear sets through a plurality of externally-meshed gears.

In addition, the present invention has been made in an effort to provide a planetary gear train of an automatic transmission for a vehicle having further advantages of enabling of setting optimum gear ratios due to ease of changing gear ratios by using a plurality of externally-meshed gears, and accordingly improving power delivery performance and fuel economy.

A planetary gear train of an automatic transmission for a vehicle according to various aspects of the present invention may include: an input shaft receiving a torque of an engine; an output shaft disposed substantially in parallel with the input shaft at a predetermined distance and outputting a changed torque; a first planetary gear set disposed on the input shaft, and including a first rotation element selectively connected to the input shaft, a second rotation element selectively connected to the input shaft and selectively operated as a fixed element, and a third rotation element operated as an output element; a second planetary gear set disposed on the output shaft, and including a fourth rotation element selectively connected to the input shaft through an externally-meshed gear, connected to the first rotation element through the externally-meshed gear, and selectively operated as a fixed element, a fifth rotation element connected to the third rotation element through an externally-meshed gear and directly connected to the output shaft, and a sixth rotation element selectively connected to the input shaft through externally-meshed gears having different gear ratios; four transfer gears forming the externally-meshed gears; and frictional elements including clutches connecting the input shaft and the rotation elements of the first and second planetary gear sets, and brakes connecting the rotation elements of the first and second planetary gear sets and a transmission housing.

In one aspect, the first planetary gear set may be a single pinion planetary gear set including a first sun gear being the first rotation element, a first planet carrier being the second rotation element, and a first ring gear being the third rotation element, and the second planetary gear set may be a single pinion planetary gear set including a second sun gear being the fourth rotation element, a second planet carrier being the fifth rotation element, and a second ring gear being the sixth rotation element.

The four transfer gears may include: a first transfer gear disposed between the first rotation element and the fourth rotation element; a second transfer gear disposed between the third rotation element and the fifth rotation element; a third transfer gear disposed between the input shaft and the sixth rotation element; and a fourth transfer gear disposed between the input shaft and the sixth rotation element.

A gear ratio of the fourth transfer gear may differ from that of the third transfer gear.

The frictional elements may include: a first clutch disposed between the third transfer gear and the sixth rotation element; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the input shaft and the fourth transfer gear; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the fourth rotation element and the transmission housing.

The first clutch and the first brake may be operated at a first forward speed, the first clutch and the second brake may be operated at a second forward speed, the first clutch and the second clutch may be operated at a third forward speed, the first clutch and the third clutch may be operated at a fourth forward speed, the second clutch and the third clutch may be operated at a fifth forward speed, the third clutch and the second brake may be operated at a sixth forward speed, the third clutch and the fourth clutch may be operated at a seventh forward speed, the fourth clutch and the second brake may be operated at an eighth forward speed, the second clutch and the fourth clutch may be operated at a ninth forward speed, and the second clutch and the first brake may be operated at a reverse speed.

In another aspect, the frictional elements may include: a first clutch disposed between the input shaft and the third transfer gear; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the input shaft and the fourth transfer gear; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the fourth rotation element and the transmission housing.

In yet another aspect, the frictional elements may include: a first clutch disposed between the third transfer gear and the sixth rotation element; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the fourth transfer gear and the sixth rotation element; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the fourth rotation element and the transmission housing.

In still another aspect, the frictional elements may include: a first clutch disposed between the third transfer gear and the sixth rotation element; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the input shaft and the fourth transfer gear; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the first rotation element and the transmission housing.

In one aspect, the first planetary gear set may be a double pinion planetary gear set including a first sun gear being the first rotation element, a first ring gear being the second rotation element, and a first planet carrier being the third rotation element, and the second planetary gear set may be a single pinion planetary gear set including a second sun gear being the fourth rotation element, a second planet carrier being the fifth rotation element, and a second ring gear being the sixth rotation element.

A planetary gear train of an automatic transmission for a vehicle according to various other aspects of the present invention may include: an input shaft receiving a torque of an engine; an output shaft disposed substantially in parallel with the input shaft at a predetermined distance and outputting a changed torque; a first planetary gear set disposed on the input shaft, and including a first rotation element selectively connected to the input shaft, a second rotation element selectively connected to the input shaft and selectively operated as a fixed element, and a third rotation element; a second planetary gear set disposed on the output shaft, and including a fourth rotation element selectively connected to the input shaft, connected to the first rotation element, and selectively operated as a fixed element, a fifth rotation element connected to the third rotation element and directly connected to the output shaft, and a sixth rotation element selectively connected to the input shaft through two paths having different gear ratios; a first transfer gear disposed between the first rotation element and the fourth rotation element; a second transfer gear disposed between the third rotation element and the fifth rotation element; a third transfer gear disposed between the input shaft and the sixth rotation element; a fourth transfer gear disposed between the input shaft and the sixth rotation element; and frictional elements including clutches connecting the input shaft and the rotation elements of the first and second planetary gear sets and brakes connecting the rotation elements of the first and second planetary gear sets and a transmission housing.

A gear ratio of the fourth transfer gear may differ from that of the third transfer gear.

In one aspect, the first planetary gear set may be a single pinion planetary gear set including a first sun gear being the first rotation element, a first planet carrier being the second rotation element, and a first ring gear being the third rotation element, and the second planetary gear set may be a single pinion planetary gear set including a second sun gear being the fourth rotation element, a second planet carrier being the fifth rotation element, and a second ring gear being the sixth rotation element.

In another aspect, the first planetary gear set may be a double pinion planetary gear set including a first sun gear being the first rotation element, a first ring gear being the second rotation element, and a first planet carrier being the third rotation element, and the second planetary gear set may be a single pinion planetary gear set including a second sun gear being the fourth rotation element, a second planet carrier being the fifth rotation element, and a second ring gear being the sixth rotation element.

In one aspect, the frictional elements may include: a first clutch disposed between the third transfer gear and the sixth rotation element; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the input shaft and the fourth transfer gear; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the fourth rotation element and the transmission housing.

In another aspect, the frictional elements may include: a first clutch disposed between the input shaft and the third transfer gear; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the input shaft and the fourth transfer gear; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the fourth rotation element and the transmission housing.

In yet another aspect, the frictional elements may include: a first clutch disposed between the third transfer gear and the sixth rotation element; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the fourth transfer gear and the sixth rotation element; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the fourth rotation element and the transmission housing.

In still another aspect, the frictional elements may include: a first clutch disposed between the third transfer gear and the sixth rotation element; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the input shaft and the fourth transfer gear; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the first rotation element and the transmission housing.

The methods and apparatuses of the present invention have other features and advantages which will be apparent from or are set forth in more detail in the accompanying drawings, which are incorporated herein, and the following Detailed Description, which together serve to explain certain principles of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic diagram of a first exemplary planetary gear train according to the present invention.

FIG. 2 is an operational chart of friction elements at each shift-speed applied to the planetary gear train of FIG. 1.

FIG. 3A is a lever diagram of the planetary gear train of FIG. 1 at the first forward speed.

FIG. 3B is a lever diagram of the planetary gear train of FIG. 1 at the second forward speed.

FIG. 3C is a lever diagram of the planetary gear train of FIG. 1 at the third forward speed.

FIG. 3D is a lever diagram of the planetary gear train of FIG. 1 at the fourth forward speed.

FIG. 3E is a lever diagram of the planetary gear train of FIG. 1 at the fifth forward speed.

FIG. 3F is a lever diagram of the planetary gear train of FIG. 1 at the sixth forward speed.

FIG. 3G is a lever diagram of the planetary gear train of FIG. 1 at the seventh forward speed.

FIG. 3H is a lever diagram of the planetary gear train of FIG. 1 at the eighth forward speed.

FIG. 3I is a lever diagram of the planetary gear train of FIG. 1 at the ninth forward speed.

FIG. 3J is a lever diagram of the planetary gear train of FIG. 1 at the reverse speed.

FIG. 4 is a schematic diagram of an exemplary planetary gear train according to the present invention.

FIG. 5 is a schematic diagram of an exemplary planetary gear train according to the present invention.

FIG. 6 is a schematic diagram of an exemplary planetary gear train according to the present invention.

FIG. 7 is a schematic diagram of an exemplary planetary gear train according to the present invention.

DETAILED DESCRIPTION

Reference will now be made in detail to various embodiments of the present invention(s), examples of which are illustrated in the accompanying drawings and described below. While the invention(s) will be described in conjunction with exemplary embodiments, it will be understood that present description is not intended to limit the invention(s) to those exemplary embodiments. On the contrary, the invention(s) is/are intended to cover not only the exemplary embodiments, but also various alternatives, modifications, equivalents and other embodiments, which may be included within the spirit and scope of the invention as defined by the appended claims.

Description of components that are not necessary for explaining the various embodiments will be omitted, and the same constituent elements are denoted by the same reference numerals in this specification. In the detailed description, ordinal numbers are used for distinguishing constituent elements having the same terms, and have no specific meanings.

FIG. 1 is a schematic diagram of a planetary gear train according to various embodiments of the present invention. Referring to FIG. 1, a planetary gear train according to various embodiments of the present invention includes a first planetary gear set PG1 disposed on an input shaft IS, a second planetary gear set PG2 disposed on an output shaft OS disposed in parallel or substantially in parallel with the input shaft IS, four transfer gears TF1, TF2, TF3, and TF4, and frictional elements consisting of four clutches C1, C2, C3, and C4 and two brakes B1 and B2.

Therefore, torque input from the input shaft IS is converted into nine forward speeds and one reverse speed by cooperation of the first and second planetary gear sets PG1 and PG2, and then is output through the output shaft OS.

The input shaft IS is an input member, and torque from a crankshaft of the engine is changed through a torque converter and is then input to the input shaft IS.

The output shaft OS is an output member and transmits driving torque to a driving wheel through a differential apparatus.

The first planetary gear set PG1 is a single pinion planetary gear set, and includes a first sun gear S1 being a first rotation element N1, a first planet carrier PC1 rotatably supporting a first pinion P1 externally meshed with the first sun gear S1 and being a second rotation element N2, and a first ring gear R1 internally meshed with the first pinion P1 and being a third rotation element N3.

The second planetary gear set PG2 is a single pinion planetary gear set, and includes a second sun gear S2 being a fourth rotation element N4, a second planet carrier PC2 rotatably supporting a second pinion P2 externally meshed with the second sun gear S2 and being a fifth rotation element N5, and a second ring gear R2 internally meshed with the second pinion P2 and being a sixth rotation element N6.

Two rotation elements of the first planetary gear set PG1 is selectively connected to the input shaft IS, three rotation elements of the second planetary gear set PG2 is connected to the input shaft IS and two rotation elements of the first planetary gear set PG1 through first, second, third, and fourth transfer gears TF1, TF2, TF3, and TF4, and any one rotation element of the second planetary gear set PG2 is directly connected to the output shaft OS.

The first, second, third, and fourth transfer gears TF1, TF2, TF3, and TF4 respectively have first, second, third, and fourth transfer drive gears TF1 a, TF2 a, TF3 a, and TF4 a and first, second, third, and fourth transfer driven gears TF1 b, TF2 b, TF3 b, and TF4 b externally meshed with each other.

The first transfer gear TF1 is disposed between the first rotation element N1 and the fourth rotation element N4. The second transfer gear TF2 is disposed between the third rotation element N3 and the fifth rotation element N5. The third transfer gear TF3 is disposed between the input shaft IS and the sixth rotation element N6. The fourth transfer gear TF4 is disposed between the input shaft IS and the sixth rotation element N6.

Therefore, the rotation elements (including the first shaft IS1) connected with each other through the first, second, third, and fourth transfer gears TF1, TF2, TF3, and TF4 are rotated in opposite directions with respect to each other according to gear ratios of the first, second, third, and fourth transfer gears TF1, TF2, TF3, and TF4.

In addition, four clutches C1, C2, C3, and C4 and two brakes B1 and B2 selectively connecting the selected rotation elements with the input shaft IS and the transmission housing H are disposed as follows.

The first clutch C1 is disposed between the third transfer gear TF3 and the sixth rotation element N6. The second clutch C2 is disposed between the input shaft IS and the first rotation element N1. The third clutch C3 is disposed between the input shaft IS and the second rotation element N2. The fourth clutch C4 is disposed between the input shaft IS and the fourth transfer gear TF4. The first brake B1 is disposed between the second rotation element N2 and the transmission housing H. The second brake B2 is disposed between the fourth rotation element N4 and the transmission housing H.

Both of the first clutch C1 and the fourth clutch C4 selectively connect the input shaft IS with the sixth rotation element N6, but rotation speeds transmitted to the sixth rotation element N6 through first clutch C1 and the fourth clutch C4 are different from each other since the gear ratio of the third transfer gear TF3 differs from the gear ratio of the fourth transfer gear TF4.

The frictional elements consisting of the first, second, third, and fourth clutches C1, C2, C3, and C4 and the first and second brakes B1 and B2 are conventional multi-plate friction elements of wet type that are operated by hydraulic pressure.

FIG. 2 is an operational chart of friction elements at each shift-speed applied to a planetary gear train according to various embodiments of the present invention. As shown in FIG. 2, two frictional elements are operated at each shift-speed in the planetary gear train according to various embodiments of the present invention.

The first clutch C1 and the first brake B1 are operated at a first forward speed 1ST. The first clutch C1 and the second brake B2 are operated at a second forward speed 2ND. The first clutch C1 and the second clutch C2 are operated at a third forward speed 3RD. The first clutch C1 and the third clutch C3 are operated at a fourth forward speed 4TH. The second clutch C2 and the third clutch C3 are operated at a fifth forward speed 5TH. The third clutch C3 and the second brake B2 are operated at a sixth forward speed 6TH. The third clutch C3 and the fourth clutch C4 are operated at a seventh forward speed 7TH. The fourth clutch C4 and the second brake B2 are operated at an eighth forward speed 8TH. The second clutch C2 and the fourth clutch C4 are operated at a ninth forward speed 9TH. The second clutch C2 and the first brake B1 are operated at a reverse speed REV.

FIG. 3A to FIG. 3J are lever diagrams of a planetary gear train according to various embodiments of the present invention, and illustrate shift processes of the planetary gear train according to various embodiments of the present invention by lever analysis method.

Referring to FIG. 3A to FIG. 3J, three vertical lines of the first planetary gear set PG2 are set to graphically represent the third, second, and first rotation elements N3, N2, and N1, and three vertical lines of the second planetary gear set PG2 are set to graphically represent the fourth, fifth, and sixth rotation elements N4, N5, and N6 from the left to the right.

A middle horizontal line represents a rotation speed of “0”, upper horizontal lines represent positive rotation speeds and lower horizontal lines represent negative rotation speeds.

“−” means that rotational elements are rotated in an opposite direction to the rotation direction of the engine. It is because the input shaft IS and the rotation elements of the first planetary gear set PG1 are externally meshed through the first, second, third, and fourth transfer gears TF1, TF2, TF3, and TF4 without an idling gear.

In addition, distances between the vertical lines of the first and second planetary gear sets PG1 and PG2 are set approximately or substantially according to gear ratios (teeth number of a sun gear/teeth number of a ring gear).

Hereinafter, referring to FIG. 2 and FIG. 3A to FIG. 3J, the shift processes of the planetary gear train according to various embodiments of the present invention will be described in detail.

First Forward Speed

Referring to FIG. 2, the first clutch C1 and the first brake B1 are operated at the first forward speed 1ST.

As shown in FIG. 3A, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the first clutch C1 and the first brake B1 are operated.

Therefore, the rotation speed of the input shaft IS is converted according to the gear ratio of the third transfer gear TF3 and is then input to the sixth rotation element N6 as an inverse rotation speed by operation of the first clutch C1, and the second rotation element N2 is operated as the fixed element by operation of the first brake B1.

Therefore, the rotation elements of the first planetary gear set PG1 form a first speed line T1 and the rotation elements of the second planetary gear set PG2 form a first shift line SP1 by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, D1 is output through the fifth rotation element N5 that is the output element.

Second Forward Speed

The first brake B1 that was operated at the first forward speed 1ST is released and the second brake B2 is operated at the second forward speed 2ND.

As shown in FIG. 3B, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the first clutch C1 and the second brake B2 are operated.

Therefore, the rotation speed of the input shaft IS IS is converted according to the gear ratio of the third transfer gear TF3 and is then input to the sixth rotation element N6 as an inverse rotation speed by operation of the first clutch C1, and the fourth rotation element N4 is operated as the fixed element by operation of the second brake B2.

Therefore, the rotation elements of the first planetary gear set PG 1 form a second speed line T2 and the rotation elements of the second planetary gear set PG2 form a second shift line SP2 by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, D2 is output through the fifth rotation element N5 that is the output element.

Third Forward Speed

The second brake B2 that was operated at the second forward speed 2ND is released and the second clutch C2 is operated at the third forward speed 3RD.

As shown in FIG. 3C, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the first clutch C1 and the second clutch C2 are operated.

Therefore, the rotation speed of the input shaft IS is converted according to the gear ratio of the third transfer gear TF3 and is then input to the sixth rotation element N6 as an inverse rotation speed by operation of the first clutch C1. In addition, the rotation speed of the input shaft IS is input to the first rotation element N1 by operation of the second clutch C2, and is converted according to the gear ratio of the first transfer gear TF1 and is then input to the fourth rotation element N4 as an inverse rotation speed.

Therefore, the rotation elements of the first planetary gear set PG1 form a third speed line T3 and the rotation elements of the second planetary gear set PG2 form a third shift line SP3 by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, D3 is output through the fifth rotation element N5 that is the output element.

Fourth Forward Speed

The second clutch C2 that was operated at the third forward speed 3RD is released and the third clutch C3 is operated at the fourth forward speed 4TH.

As shown in FIG. 3D, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the first clutch C1 and the third clutch C3 are operated.

Therefore, the rotation speed of the input shaft IS is converted according to the gear ratio of the third transfer gear TF3 and is then input to the sixth rotation element N6 as an inverse rotation speed by operation of the first clutch C1. In addition, the rotation speed of the input shaft IS is directly input to the second rotation element N2 by operation of the third clutch C3.

Therefore, the rotation elements of the first planetary gear set PG1 form a fourth speed line T4 and the rotation elements of the second planetary gear set PG2 form a fourth shift line SP4 by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, D4 is output through the fifth rotation element N5 that is the output element.

Fifth Forward Speed

The first clutch C1 that was operated at the fourth forward speed 4TH is released and the second clutch C2 is operated at the fifth forward speed 5TH.

As shown in FIG. 3E, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the second clutch C2 and the third clutch C3 are operated.

Therefore, the rotation speed of the input shaft IS is directly input to the first rotation element N1 by operation of the second clutch C2, is converted according to the gear ratio of the first transfer gear TF1 and is then input to the fourth rotation element N4 as an inverse rotation speed. In addition, the rotation speed of the input shaft IS is directly input to the second rotation element N2 by operation of the third clutch C3.

Therefore, the first planetary gear set PG1 becomes a direct-coupling state, the rotation elements of the first planetary gear set PG1 form a fifth speed line T5, and the rotation elements of the second planetary gear set PG2 form a fifth shift line SP5 by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, D5 is output through the fifth rotation element N5 that is the output element.

Sixth Forward Speed

The second clutch C2 that was operated at the fifth forward speed 5TH is released and the second brake B2 is operated at the sixth forward speed 6TH.

As shown in FIG. 3F, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the third clutch C3 and the second brake B2 are operated.

Therefore, the rotation speed of the input shaft IS is directly input to the second rotation element N2 by operation of the third clutch C3, and the first and fourth rotation element N1 and N4 are operated as the fixed elements by operation of the second brake B2.

Therefore, the rotation elements of the first planetary gear set PG1 form a sixth speed line T6 and the rotation elements of the second planetary gear set PG2 form a sixth shift line SP6 by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, D6 is output through the fifth rotation element N5 that is the output element.

Seventh Forward Speed

The second brake B2 that was operated at the sixth forward speed 6TH is released and the fourth clutch C4 is operated at the seventh forward speed 7TH.

As shown in FIG. 3G, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the third clutch C3 and the fourth clutch C4 are operated.

Therefore, the rotation speed of the input shaft IS is directly input to the second rotation element N2 by operation of the third clutch C3, and is converted according to the gear ratio of the fourth transfer gear TF4 and is then input to the sixth rotation element N6 as an inverse rotation speed by operation of the fourth clutch C4.

Therefore, the rotation elements of the first planetary gear set PG1 form a seventh speed line T7 and the rotation elements of the second planetary gear set PG2 form a seventh shift line SP7 by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, D7 is output through the fifth rotation element N5 that is the output element.

Eighth Forward Speed

The third clutch C3 that was operated at the seventh forward speed 7TH is released and the second brake B2 is operated at the eighth forward speed 8TH.

As shown in FIG. 3H, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the fourth clutch C4 and the second brake B2 are operated.

Therefore, the rotation speed of the input shaft IS is converted according to the gear ratio of the fourth transfer gear TF4 by operation of the fourth clutch C4 and is then input to the sixth rotation element N6 as an inverse rotation speed. In addition, the first and fourth rotation elements N1 and N4 are operated as the fixed elements by operation of the second brake B2.

Therefore, the rotation elements of the first planetary gear set PG1 form an eighth speed line T8 and the rotation elements of the second planetary gear set PG2 form an eighth shift line SP8 by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, D8 is output through the fifth rotation element N5 that is the output element.

Ninth Forward Speed

The second brake B2 that was operated at the eighth forward speed 8TH is released and the second clutch C2 is operated at the ninth forward speed 9TH.

As shown in FIG. 3I, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the fourth clutch C4 and the second clutch C2 are operated.

Therefore, the rotation speed of the input shaft IS is directly input to the first rotation element N1 by operation of the second clutch C2, and is converted according to the gear ratio of the first transfer gear TF1 and is then input to the fourth rotation element N4 as an inverse rotation speed. In addition, the rotation speed of the input shaft IS is converted according to the gear ratio of the fourth transfer gear TF4 by operation of the fourth clutch C4 and is then input to the sixth rotation element N6 as an inverse rotation speed.

Therefore, the rotation elements of the first planetary gear set PG1 form a ninth speed line T9 and the rotation elements of the second planetary gear set PG2 form a ninth shift line SP9 by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, D9 is output through the fifth rotation element N5 that is the output element.

Reverse Speed

As shown in FIG. 2, the second clutch C2 and the first brake B1 are operated at the reverse speed REV.

As shown in FIG. 3J, in a state that the third rotation element N3 is connected to the fifth rotation element N5 through the second transfer gear TF2 and the first rotation element N1 is connected to the fourth rotation element N4 through the first transfer gear TF1, the second clutch C2 and the first brake B1 are operated.

Therefore, the rotation speed of the input shaft IS is directly input to the first rotation element N1 by operation of the second clutch C2, and is converted according to the gear ratio of the first transfer gear TF1 and is then input to the fourth rotation element N4 as an inverse rotation speed. In addition, the second rotation element N2 is operated as the fixed element by operation of the first brake B1.

Therefore, the rotation elements of the first planetary gear set PG1 form a reverse speed line Tr and the rotation elements of the second planetary gear set PG2 form a reverse shift line RS by cooperation of the first planetary gear set PG1 and the second planetary gear set PG2. Therefore, REV is output through the fifth rotation element N5 that is the output element.

As described above, the planetary gear train according to various embodiments of the present invention can achieve nine forward speeds and one reverse speed by combining two planetary gear sets PG1 and PG2 being the simple planetary gear sets, four transfer gears TF1, TF2, TF3, and TF4 being the externally-meshed gears and six frictional elements C1, C2, C3, C4, B1, and B2.

In addition, optimum gear ratios may be set due to ease of changing gear ratios by using four transfer gears being externally-meshed gears as well as the planetary gear sets. Since gear ratios can be changed according to target performance, starting performance, power delivery performance and fuel economy may be improved. Therefore, a start-up clutch instead of a torque converter may be used.

In addition, two friction elements are operated at each shift-speed and one friction element is released and another friction element is operated so as to shift to a neighboring shift-speed. Therefore, shift control condition is fully satisfied.

FIG. 4 is a schematic diagram of a planetary gear train according to various embodiments of the present invention. Referring to FIG. 4, the first clutch C1 is disposed between the input shaft IS and the third transfer gear TF3 in the presently described embodiment, while the first clutch C1 is disposed between the third transfer gear TF3 and the sixth rotation element N6 in the first described embodiment.

Since functions of such embodiments are the same as those of the first described embodiment except the position of the first clutch C1, detailed description thereof will be omitted.

FIG. 5 is a schematic diagram of a planetary gear train according to various embodiments of the present invention. Referring to FIG. 5, the fourth clutch C4 is disposed between the fourth transfer gear TF4 and the sixth rotation element N6 in such embodiments, while the fourth clutch C4 is disposed between the input shaft IS and the fourth transfer gear TF4 in the first described embodiment.

Since functions of such embodiments are the same as those of the first described embodiment except the position of the fourth clutch C4, detailed description thereof will be omitted.

FIG. 6 is a schematic diagram of a planetary gear train according to various embodiments of the present invention. Referring to FIG. 6, the second brake B2 is disposed between the first rotation element N1 and the transmission housing H in such embodiments, while the second brake B2 is disposed between the fourth rotation element N4 and the transmission housing H in the first described embodiment.

Since functions of such embodiments are the same as those of the first described embodiment except the position of the second brake B2, detailed description thereof will be omitted.

FIG. 7 is a schematic diagram of a planetary gear train according to various embodiments of the present invention. Referring to FIG. 7, the first planetary gear set PG1 is a double pinion planetary gear set in such embodiments, while the first planetary gear set PG1 is the single pinion planetary gear set in the first described embodiment.

Therefore, the second rotation element N2 is changed from the first planet carrier PC1 to the first ring gear R1 and the third rotation element N3 is changed from the first ring gear R1 to the first planet carrier PC1.

Since functions of such embodiments are the same as those of the first described embodiment except the rotation elements consisting of the second and third rotation elements N2 and N3, detailed description thereof will be omitted.

Nine forward speeds and one reverse speed can be achieved by combining two planetary gear sets being the simple planetary gear sets, four transfer gears and six frictional elements.

In addition, since two planetary gear sets are disposed separately on the input shaft and the output shaft disposed in parallel or substantially in parallel with a predetermined distance, a length thereof may be reduced and mountability may be improved.

In addition, optimum gear ratios may be set due to ease of changing gear ratios by using four external-meshing gears as well as the planetary gear sets. Since gear ratios can be changed according to target performance, starting performance, power delivery performance, and fuel economy may be improved. Therefore, a start-up clutch instead of a torque converter may be used.

In addition, two friction elements are operated at each shift-speed, and one friction element is released and another friction element is operated so as to shift to a neighboring shift-speed. Therefore, shift control condition is fully satisfied.

For convenience in explanation and accurate definition in the appended claims, the terms “upper” or “lower”, and etc. are used to describe features of the exemplary embodiments with reference to the positions of such features as displayed in the figures.

The foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description. They are not intended to be exhaustive or to limit the invention to the precise forms disclosed, and obviously many modifications and variations are possible in light of the above teachings. The exemplary embodiments were chosen and described in order to explain certain principles of the invention and their practical application, to thereby enable others skilled in the art to make and utilize various exemplary embodiments of the present invention, as well as various alternatives and modifications thereof. It is intended that the scope of the invention be defined by the Claims appended hereto and their equivalents. 

What is claimed is:
 1. A planetary gear train of an automatic transmission for a vehicle, comprising: an input shaft receiving a torque of an engine; an output shaft disposed in parallel with the input shaft at a predetermined distance and outputting a changed torque; a first planetary gear set disposed on the input shaft, and including a first rotation element selectively connectable to the input shaft, a second rotation element selectively connectable to the input shaft and selectively connectable to a transmission housing, and a third rotation element; a second planetary gear set disposed on the output shaft, and including a fourth rotation element selectively connectable to the input shaft, connected to the first rotation element, and selectively connectable to the transmission housing, a fifth rotation element connected to the third rotation element and directly connected to the output shaft, and a sixth rotation element selectively connectable to the input shaft; a first transfer gear directly connecting the first rotation element with the fourth rotation element; a second transfer gear directly connecting the third rotation element with the fifth rotation element; a third transfer gear connected to the input shaft and selectively connectable to the sixth rotation element; and four transfer gears selectively connectable to the input shaft and continuously connected to the sixth rotation element.
 2. The planetary gear train of claim 1, wherein the first planetary gear set is a single pinion planetary gear set including a first sun gear being the first rotation element, a first planet carrier being the second rotation element, and a first ring gear being the third rotation element, and the second planetary gear set is a single pinion planetary gear set including a second sun gear being the fourth rotation element, a second planet carrier being the fifth rotation element, and a second ring gear being the sixth rotation element.
 3. The planetary gear train of claim 2, wherein the first transfer gear is disposed between the first rotation element and the fourth rotation element; the second transfer gear is disposed between the third rotation element and the fifth rotation element; the third transfer gear is disposed between the input shaft and the sixth rotation element; and the fourth transfer gear is disposed between the input shaft and the sixth rotation element.
 4. The planetary gear train of claim 3, wherein a gear ratio of the fourth transfer gear differs from that of the third transfer gear.
 5. The planetary gear train of claim 3, wherein a first clutch is disposed between the third transfer gear and the sixth rotation element; a second clutch is disposed between the input shaft and the first rotation element; a third clutch is disposed between the input shaft and the second rotation element; a fourth clutch is disposed between the input shaft and the fourth transfer gear; a first brake is disposed between the second rotation element and the transmission housing; and a second brake is disposed between the fourth rotation element and the transmission housing.
 6. The planetary gear train of claim 5, wherein the first clutch and the first brake are operated at a first forward speed, the first clutch and the second brake are operated at a second forward speed, the first clutch and the second clutch are operated at a third forward speed, the first clutch and the third clutch are operated at a fourth forward speed, the second clutch and the third clutch are operated at a fifth forward speed, the third clutch and the second brake are operated at a sixth forward speed, the third clutch and the fourth clutch are operated at a seventh forward speed, the fourth clutch and the second brake are operated at an eighth forward speed, the second clutch and the fourth clutch are operated at a ninth forward speed, and the second clutch and the first brake are operated at a reverse speed.
 7. The planetary gear train of claim 3, wherein the frictional elements comprise: a first clutch disposed between the third transfer gear and the sixth rotation element; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the input shaft and the fourth transfer gear; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the first rotation element and the transmission housing.
 8. A planetary gear train of an automatic transmission for a vehicle, comprising: an input shaft receiving a torque of an engine; an output shaft disposed in parallel with the input shaft at a predetermined distance and outputting changed torque; a first planetary gear set disposed on the input shaft, and including a first rotation element selectively connectable to the input shaft, a second rotation element selectively connectable to the input shaft and selectively connectable to a transmission housing, and a third rotation element; a second planetary gear set disposed on the output shaft, and including a fourth rotation element selectively connectable to the input shaft, connected to the first rotation element, and selectively connectable to the transmission housing, a fifth rotation element connected to the third rotation element and directly connected to the output shaft, and a sixth rotation element selectively connectable to the input shaft; a first clutch selectively connecting the input shaft with the sixth rotation element; a second clutch selectively connecting the input shaft with the first rotation element; a third clutch selectively connecting the input shaft with the second rotation element; a fourth clutch selectively connecting the input shaft with the sixth rotation element; a first brake selectively connecting the second rotation element with the transmission housing; a second brake selectively connecting the fourth rotation element with the transmission housing; a first transfer gear directly connected to the first rotation element and the fourth rotation element; a second transfer gear directly connected to the third rotation element and the fifth rotation element; a third transfer gear connected to the input shaft and the first clutch; a fourth transfer gear connected to the fourth clutch and continuously connected to the sixth rotation element.
 9. The planetary gear train of claim 8, wherein a gear ratio of the fourth transfer gear differs from that of the third transfer gear.
 10. The planetary gear train of claim 8, wherein the first planetary gear set is a single pinion planetary gear set including a first sun gear being the first rotation element, a first planet carrier being the second rotation element, and a first ring gear being the third rotation element, and the second planetary gear set is a single pinion planetary gear set including a second sun gear being the fourth rotation element, a second planet carrier being the fifth rotation element, and a second ring gear being the sixth rotation element.
 11. The planetary gear train of claim 8, wherein the first clutch is disposed between the third transfer gear and the sixth rotation element; the second clutch is disposed between the input shaft and the first rotation element; the third clutch is disposed between the input shaft and the second rotation element; the fourth clutch is disposed between the input shaft and the fourth transfer gear; the first brake disposed between the second rotation element and the transmission housing; and the second brake disposed between the fourth rotation element and the transmission housing.
 12. The planetary gear train of claim 8, wherein the frictional elements comprise: a first clutch disposed between the third transfer gear and the sixth rotation element; a second clutch disposed between the input shaft and the first rotation element; a third clutch disposed between the input shaft and the second rotation element; a fourth clutch disposed between the input shaft and the fourth transfer gear; a first brake disposed between the second rotation element and the transmission housing; and a second brake disposed between the first rotation element and the transmission housing. 